Cam-controlled continuously variable transmission system

Abstract

An arrangement for balancing axial forces in a drive clutch and a driven clutch of a continuously variable transmission system, the continuously variable transmission system may include, but is not limited to, a pulley, a sheave mechanism, a drive clutch mechanism or drive clutch, a driven sheave mechanism, a driven clutch mechanism or driven clutch, and a shift mechanism, servo mechanism, actuator mechanism or actuator. Torque transmitted by the continuously variable transmission system is converted into an axial force acting on the belt. Forces in the driving clutch and the driven clutch are balanced to minimize the force required by the shift mechanism to change the speed.

Description

Technical Field

[0001] The present invention relates to continuously variable transmissions and systems and methods of manufacture controlled by using a cam system to balance the axial forces in the driving and driven clutches. More specifically, the present invention relates to cam-controlled CVT systems for applications such as automotive, industrial, and personal mobility (such as bicycles). Background Art

[0002] In many applications utilizing a driven sprocket and a drive sprocket or crankshaft, the ability to change gear ratios is unavailable or complicated and the gear ratios must be changed using individual sprockets of different sizes and a system, such as a derailleur, to move the chain or belt from each sprocket. This can be expensive, add complexity to the system, and result in additional points of failure within the system. It is also difficult to optimize the drive system for a wide range of operating conditions.

[0003] Embodiments of the present invention do not rely on multiple sprockets and a derailleur to change gear ratios. Instead, the embodiments described herein have multiple sets of sheaves connected by a belt that continuously moves between a potentially infinite number of speed ratios, allowing the user to specifically select the best speed ratio for the current operating conditions. "Speed ​​ratio" describes the relative mechanical advantage between the multiple sets of sheaves and is similar to a gear ratio.

[0004] However, in a conventional continuously variable transmission, a large amount of torque is generated in the system, which requires a large amount of force to change the speed ratio. The present invention utilizes a cam-controlled actuator to balance the forces in the drive clutch and the driven clutch to minimize the force required to change the speed ratio. By balancing the forces in the driven clutch and the drive clutch, the axial force acting on the belt by the transmitted torque is also reduced, which can increase belt life and reduce belt noise. Summary of the invention

[0005] The present invention summary is provided to introduce in a simplified form a selection of concepts that will be further described in the following specific embodiments. The present invention summary and the foregoing background technology are not intended to identify key aspects or essential aspects of the claimed subject matter. In addition, the present invention summary is not intended to be used to help determine the scope of the claimed subject matter.

[0006] The present disclosure relates to continuously variable transmissions, such as for use in automobiles, electric bicycles, and other personal mobility systems, such as standard bicycles, wheelchairs, scooters including electric scooters, motorcycles, and other systems that utilize belts to transfer power to impart motion to the system. The present disclosure provides a system that utilizes a cam-controlled continuously variable transmission system to balance axial forces in a drive clutch and a driven clutch.

[0007] These and other aspects of the technology described herein will become apparent after considering the detailed description and drawings herein. However, it should be understood that the scope of the subject matter claimed should be determined by the issued claims, rather than by whether a given subject matter solves any or all of the problems mentioned in the background technology or includes any features or aspects listed in the summary of the invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Non-limiting and non-exhaustive embodiments of the disclosed technology are described with reference to the following figures, wherein like reference numerals refer to like parts throughout the various views unless otherwise specified.

[0009] Figure 1 A rear isometric view of an exemplary embodiment of a cam-controlled continuously variable transmission system.

[0010] Figure 2 A front view of an exemplary embodiment of a cam-controlled continuously variable transmission system.

[0011] Figure 3 It is a side view of an exemplary embodiment of a cam-controlled continuously variable transmission of the present invention.

[0012] Figure 4 is a side view of an exemplary embodiment of a drive clutch without a movable sheave, without a bearing and without a bearing carrier.

[0013] Figure 5 Side view of a sleeve with slots and pins for actuating a clutch mechanism, showing the force distribution.

[0014] Figure 6 for Figure 4 A cross-sectional view of a drive clutch mechanism taken along line AA, wherein the drive clutch mechanism includes a movable sheave, a bearing and a bearing carrier.

[0015] Figure 7 is a side view of an exemplary embodiment of a driven clutch mechanism.

[0016] Figure 8 for Figure 7 A cross-sectional view of the driven clutch mechanism taken along line BB.

[0017] Fig. 9 is a side view of an exemplary embodiment of a driven clutch mechanism that does not include a movable sheave or spring.

[0018] Fig.10 A side view of an exemplary embodiment of a sleeve with slots and pins for a driven clutch mechanism showing the distribution of forces.

[0019] Fig.11 is a side view of an exemplary embodiment of a driven clutch mechanism with hidden slots shown by dashed lines.

[0020] Fig.12 A side view of an exemplary embodiment of a cam-controlled continuously variable transmission system showing belt lateral and balancing forces.

[0021] Fig.13 A side view of an exemplary embodiment of a cam-controlled continuously variable transmission showing the distribution of forces acting on a slot, with the movable sheave and belt shown by dashed lines.

[0022] Fig.14 A side view of a drive clutch having another embodiment of an actuation mechanism.

[0023] Fig.15 for Fig.14 Rear isometric view of the drive clutch shown in .

[0024] Fig.16 A partial expanded view of the constant angle slots in the drive and driven clutches of an alternative embodiment of a cam controlled continuously variable transmission system, expanded at radius R.

[0025] Fig.17 A partial expanded view at radius R of variable slot angles in a drive clutch and a driven clutch of an exemplary embodiment of a cam-controlled continuously variable transmission system.

[0026] Fig.18 A partial expanded view of a slot at radius R for an alternative embodiment of a cam-controlled continuously variable transmission system.

[0027] Fig.19 A partial expanded view of a slot at radius R for another alternative embodiment of a cam-controlled continuously variable transmission system.

[0028] Fig. 20 A partial expanded view at radius R of a slot cooperating with two pins for an alternative embodiment of a cam-controlled continuously variable transmission system.

[0029] Fig.21 A partial expanded view of the slots at radius R of an alternative embodiment of a cam-controlled continuously variable transmission system, the slots being angularly and axially spaced from one another.

[0030] Fig. 22 A partial expanded view of a slot at radius R of an alternative embodiment of a cam controlled continuously variable transmission system, wherein one side of the slot is open.

[0031] It should be understood that the drawings are not necessarily drawn to scale and that various dimensions may vary. In some cases, details that are not necessary for understanding the present invention or that make other details difficult to understand may have been omitted. Of course, it should be understood that the present invention is not necessarily limited to the specific embodiments illustrated herein.

[0032] A1-Angle FR2-Radial Force S51 - Side of the slot A2-Angle FX2-Axial force S52-Side of the slot SA-angle TFX1-Total axial force S53-Side of the slot SA1-Angle TFX2-Total Axial Force 2-axis SA2-Angle BF-band force 4-Drive sleeve AX - axis of rotation BFX1-Axial force of belt 8-Fixed sheave AX1-axis BFX2-Axial force of belt 10- Movable sheave AX2-axis R-Cam radius 12-Pin D1 - Direction of rotation S1-Slot 12X-axis D3-direction S2-Slot 14-Bearing FN1 - Normal force S3-Slot 16-Carrier FR1-Radial force S4-Slot 16B-Carrier FX1-Axial force S3B - Slot start 16C-Cavity FN2 - Normal force S5-Slot 18-Retaining ring 20-Bushing / Bearing 34-Fixed sheave 42-Actuator Arm 22-Retaining ring 36-Output shaft 43-Axis 24-O-ring / seal ring 36B-Flange 44-Connecting rod 30-Speed ​​sensor 38-Spring 46- Shell 32-Movable sheave 39-Driven sheave 48-Bolt 33-Pin S39-Slot 50-Belt 33X-axis 40-Actuator 52-Eccentric wheel DETAILED DESCRIPTION

[0033] As described above, the present specification relates to continuously variable transmissions and systems and methods of manufacture that are controlled by using a cam system to balance the axial forces in the drive clutch and the driven clutch. More specifically, the present application relates to cam-controlled CVT systems for applications such as automotive, industrial, and personal mobility (such as bicycles).

[0034] In the following description, reference is made to the accompanying drawings, which form a part of the description and in which at least one specific embodiment is shown by way of example. The following description provides additional specific embodiments. These embodiments are disclosed in sufficient detail to enable those skilled in the art to practice the invention. It should be understood that other embodiments may be conceived and made without departing from the scope or spirit of the present disclosure. Therefore, the following detailed description should not be considered restrictive. Although the present disclosure is not limited thereto, an understanding of various aspects of the present disclosure will be obtained through a discussion of the examples provided below, including the accompanying drawings. In some cases, a figure mark may have an associated sub-label consisting of lowercase letters to represent one of a plurality of similar components. When a figure mark without a sub-label description is referenced, the reference is intended to refer to all such multiple similar components.

[0035] like Figure 1 , 2 As shown in and 3, an embodiment of a continuously variable transmission system or CVT system may include but is not limited to at least one pulley, at least one sheave mechanism, a driving clutch mechanism or a driving clutch 100, a driven pulley mechanism, a driven clutch mechanism or a driven clutch 200, and a shifting mechanism, a servo mechanism, an actuator mechanism or an actuator 300.

[0036] In some embodiments, the driving clutch 100 can be connected to the driven clutch 200 via a belt 50. The belt 50 can be a type of endless belt, segmented belt, etc. The belt 50 can transfer power from the driving clutch to the driven clutch. The speed sensor 30 is fixedly attached to the housing 46 (attachments not shown) to monitor the rotational speed of the driven clutch and the driving clutch.

[0037] In some embodiments, Figure 4 , 5As shown in Figures 1 and 6, the drive clutch 100 may include, but is not limited to, an input shaft or drive shaft 2, a fixed sheave 8 fixedly attached to the shaft 2 (in some embodiments, this may be achieved by utilizing a press fit), a drive sleeve 4 movably journaled to the shaft 2, and a round pin 12 rotatably journaled to a hole in the shaft 2, wherein the upper portion of the round pin 12 loosely engages a slot S4 formed in the drive sleeve 4. In another embodiment (not shown), the pin may be replaced by a roller. In yet another embodiment (not shown), the pin may be replaced by a slide.

[0038] Sealing rings 24, such as but not limited to O-rings, are located in grooves formed on the inner diameter of the drive sleeve 4, located near each end of the drive sleeve 4. The sealing rings prevent grease (not shown) that may fill the slots S4 from flowing to the outside, which may cause accelerated wear of the system.

[0039] The movable second drive sheave 10 is fixedly attached to the drive sleeve 4 so it moves with the drive sleeve 4. The inner diameter of the thrust bearing 14 is fixedly attached to the outer diameter of the rod of the movable second drive sheave 10. The retaining ring 18 prevents the bearing 14 from sliding out of the movable second drive sheave 10. The carrier 16 is fixedly attached to the outer diameter of the bearing 14. In one embodiment, the bearing 14 can be a ball bearing type bearing, but can also be a roller or needle bearing. In other embodiments, the bearing 14 can be a coated bushing configured to act as a ball bearing.

[0040] The drive shaft 2, the fixed first drive sheave 8, the movable second drive sheave 10, the drive sleeve 4, and the pin 12 can be made of a steel alloy, however, in some embodiments, these components can be made of other metals, such as aluminum alloys, titanium alloys; made of polymers, such as but not limited to ABS or HDPE; or made of composite materials, such as but not limited to carbon fiber reinforced composite materials. In some embodiments, two pins 12 spaced approximately 180 degrees apart may be beneficial. In other embodiments, more pins and corresponding slots can be used to transmit high torque in applications where required.

[0041] like Figure 6 As shown in FIG, the bearing 20 is rotatably journaled on the drive sleeve 4 and is prevented from sliding out of the drive sleeve 4 by a retaining ring 22. The bearing 20 may be a roller bearing, a needle bearing, or a polymer, composite, or metal bushing. When the sheaves 8 and 10 are separated to their maximum open position (not shown), the bearing 20 supports the inner surface of the belt 50.

[0042] like Figure 7 and Figure 8As shown in the figure, the driven clutch 200 includes an output shaft 36, a fixed groove wheel 34 fixedly attached to the shaft 36 (in some embodiments, this can be achieved by using a press fit), a groove wheel 32 movably journaled to the shaft 36, and a round pin 33 rotatably journaled to a hole in the shaft 36, wherein the upper portion of the round pin loosely engages a narrow slot S39 formed in a driven sleeve 39.

[0043] In some embodiments, a compression spring 38 is slidably journaled on a rod of the movable sheave 32. One end of the spring 38 pushes the sheave 32 toward the fixed first driven sheave 34, while the other end of the spring 38 abuts against a flange 36B formed at one end of the shaft 36. The shaft 36, the fixed first driven sheave 34, the movable second driven sheave 32, the driven sleeve 39, and the pin 33 can be made of a steel alloy, however, in some embodiments, these components can be made of other metals, such as but not limited to aluminum alloys and titanium alloys; made of polymers, such as but not limited to ABS or HDPE; or made of composite materials, such as but not limited to carbon fiber reinforced composite materials. In some embodiments, the CVT cam system can include three pins 33 spaced 120 degrees apart. In other embodiments, more pins can be used to transmit higher torques.

[0044] like Figure 1 and Figure 3 As shown in , the actuator mechanism 300 can include an actuator motor 40, an actuator arm 42 fixedly attached to an output shaft 43 of the actuator motor. One end of the actuator arm 42 can be rotatably journaled with a connecting rod 44. The other end of the connecting rod 44 can be rotatably journaled with the carrier 16. The actuator motor 40 can be fixedly attached to the housing or shell 46 by bolts 48 or other fastening systems (such as but not limited to press-fit pins, rivets, etc.). In some embodiments, it may be beneficial for the carrier to be a driving carrier and in other embodiments a driven carrier. The bearings can be thrust bearings, roller bearings, needle bearings, etc.

[0045] Fig.14 and Fig.15Another embodiment of an actuator mechanism is shown, which includes a cam or eccentric wheel 52 rigidly attached to the actuator motor output shaft 43. The eccentric wheel 52 cooperates with the side of the cavity 16C formed in the carrier 16B. In another embodiment, the actuator mechanism may include a lead screw for force multiplication. In some embodiments of the cam-controlled continuously variable transmission system, the actuator can be engaged with the carrier through an eccentric wheel, wherein the eccentric wheel is rigidly attached to the output shaft of the actuator and is engaged in a cooperative manner with the carrier. In some embodiments, the eccentric wheel can be a cam. In some embodiments of the cam-controlled continuously variable transmission system, the actuator can include a screw for force multiplication. The actuator can also actuate a second drive sheave. The actuator can be configured to move the second driven sheave axially along the driven shaft.

[0046] like Figure 1 and Figure 2 As shown in , the input power is transmitted to the drive clutch 100 via the drive shaft 2 rotating in the direction D1. According to an embodiment, the input power can come from an internal combustion engine, an electric motor, a hydraulic motor, a pneumatic motor, human power (such as a pedal or crank of a bicycle or other personal mobility system), or any type of input power transmitted in the form of rotational motion. The drive shaft can be connected to any input power device, including but not limited to an internal combustion engine, an electric motor, a hydraulic motor, a pneumatic motor, human power (such as a pedal or crank of a bicycle or other personal mobility system), or any type of input power transmitted in the form of rotational motion.

[0047] like Figure 4 , 5 As shown in Figures 1 and 6, at least one pin 12 is rotatably journaled in a hole of the shaft 2 to apply a force on a side of a slot S4 formed in the drive sleeve 4. One side of the slot S4 can be oriented at an angle A1 relative to the shaft axis AX1. The force FN1 is orthogonal to the side of the slot S4. The force FN1 is resolved into an axial force FX1, which pushes the drive sleeve 4 and the movable second drive sheave 10 attached thereto toward the belt 50 along the axis AX1. The force FN1 is also resolved into a radial force FR1, which causes the drive sleeve 4 and the second drive sheave 10 attached thereto to rotate in a direction D1. As a result, the belt 50 is compressed between the fixed first drive sheave 8 and the movable second drive sheave 10. The squeezing force allows the friction on both sides of the belt 50 to rotate via Fig.14 The band force BF shown in FIG. 1 transfers torque to the driven clutch 200 .

[0048] The sum of all axial forces FX1 is denoted as TFX1 and is Fig.12In some embodiments, the CVT cam system may include two slots S4 and two pins, one pin in each slot, so in such an embodiment TFX1 is:

[0049]

[0050] like Figure 2 , Fig.10 ,as well as Fig.13 As shown in , the force BF of the belt causes a normal force FN2. Fig.10 As shown in FIG. 1 , force FN2 acts on the side surface of slot S39. The side of slot S39 may be oriented at an angle A2 relative to axis AX2. Force FN2 is a reaction force between pin 33 and the side of slot S39. Force FN2 is decomposed into axial force FX2 and radial force FR2. The sum of all axial forces FX2 from all pins 33 is identified as TFX2 (in Fig.12 ), said TFX2 generates most of the axial force BFX2 of the balancing belt. The spring 38 pushes against the second driven sheave 32 with a spring force SF. The spring force SF is added to the entire axial force FX2, as shown in the following equation:

[0051]

[0052]

[0053] Compared to the axial force TFX2, the magnitude of the force SF is small. In one embodiment, the spring force SF may fluctuate between 1 / 20 and 1 / 10 of the force TFX2. In some embodiments, the function of the spring 38 may be to ensure that contact is maintained between the belt 50 and the second driven sheave 32 and the first driven sheave 34 before torque is applied to the shaft 2, so that the CVT system of the present invention can begin to transmit torque without belt slippage. Once the torque is applied, the axial force generated on the surface of the slot S4 and the surface of the slot S39 may be optimally proportional to the torque, and therefore sufficient to transmit torque via the belt 50 without belt slippage. In one embodiment, the spring 38 may be a helical spring, a torsion spring, a wave spring, or the like. In some embodiments of a cam-controlled continuously variable transmission system, the force applied by the actuator may roughly correspond to the contact area between the belt and the second drive sheave and the second driven sheave, thereby offsetting the force of the belt acting on the second drive sheave and the second driven sheave.

[0054] The contact radius between the belt and the sheaves in the drive clutch and the driven clutch changes in response to input from the actuator mechanism 300, thereby accelerating or decelerating the driven clutch compared to the drive clutch of the changing speed ratio. The change in the contact radius between the belt and the sheave is achieved by moving the second drive sheave 10 along the rotation axis AX1. Figure 3 and Figure 6 As shown in , the second drive sheave 10 is axially moved by the actuator mechanism 300. To accomplish this action, the arm 42 is attached to the motor shaft 43 and changes the position of the connecting rod 44 in response to the rotation of the motor shaft 43 when actuated. In some embodiments, the connecting rod 44 rotatably journaled with the carrier 16 acts on the second drive sheave 10 via the thrust bearing 14. In some embodiments, the actuator can engage with the carrier through a connecting rod rotatably journaled with the carrier.

[0055] like Figure 5 and Fig.13 As shown in , the force required by the actuator motor 40 to change the axial position of the second drive sheave 10 is minimized by the axial force FX1 generated on the surface of the slot S4. The angle A1 is such that the sum of the forces S4 from all pins 12 approximately balances the axial force BFX1 of the belt. This minimizes and optimizes the power requirements of the actuator motor 40, thereby making the size, weight, and power consumption of the actuator motor 40 small. In some embodiments, the actuator motor can be a stepper motor, a servo motor, a DC brushless motor, a DC brushed motor, a direct drive motor, etc.

[0056] In some embodiments, angle A2 is such that the sum of the forces FX2 generated by all pins 33 on the surface of slot S39 approximately balances the axial force BFX2 of the belt. Fig.16 , 17 , 18, 19, 20 and Fig. 22 The expanded views of different embodiments of the slots S4 and S39 are shown. Figure 6 It is obtained at the radius R shown in . Fig.16 An expanded view of an alternative embodiment of a spiral slot S1 is shown. The slot S1 is oriented at a constant angle SA1 relative to the rotation axis AX along its entire length. In some embodiments of a cam-controlled continuously variable transmission system, it may be beneficial to have a first portion or starting angular portion of at least one drive slot parallel to the rotation axis.

[0057] In some embodiments of a cam-controlled continuously variable transmission system, it may be beneficial to keep the drive slot angle and the driven slot angle constant. In other cases, it may be beneficial to have the drive slot angle and the driven slot angle have variable angles. In some embodiments, this can be achieved by having a starting angle in the drive clutch of approximately 16 degrees at the first end of at least one drive slot and gradually increasing to an angle in the range of 38 degrees at the second end of at least one drive slot, and a starting slot angle in at least one driven slot of approximately 60 degrees at the first end and gradually decreasing to an angle in the range of 35 degrees at the second end of at least one driven slot.

[0058] In most applications, the amount of axial force acting on the belt may depend on the radius of the belt contact sheave. If too much force is applied, it may cause excessive stress on the CVT system and premature belt wear. If too little force is applied, it may cause belt slippage, which may lead to belt failure. Fig.17 An expanded view of the slot S2 is shown that helps optimize the magnitude of the axial force. In some embodiments, the slot S2 can have a variable angle along its length. At one end of the slot, the angle SA2 is greater than the angle SA3 at the opposite end of the slot. The slot angle gradually changes between angles SA2 and SA3 along the length of the slot S2. This causes the axial force FX1 in the drive clutch and the axial force FX2 in the driven clutch to vary depending on the axial position of the pins 12 and 33 inside the slots.

[0059] In some embodiments, the angles of the slots in the drive clutch and the slots in the driven clutch are calculated to balance the forces of the band in order to obtain optimal band compression and stable operation of the CVT system. In one embodiment, the slot angle SA3 (drive clutch side) in the initial stage is about 16 degrees, and the slot angle SA2 is about 33 degrees. The slot in the driven clutch can have an angle SA3 of about 60 degrees and a slot angle SA2 of about 30 degrees. In some embodiments, the approximate angle range can be within plus or minus 5 degrees of the stated values, depending on the parameters to be optimized.

[0060] Fig.18 An expanded view of another embodiment of a slot designated as S3 is shown. The slot S3 preferably has a variable angle along its length and a short portion S3B that is generally parallel to the axis of rotation. When portion S3B is engaged with pin 12, no axial force is generated on the surface of the slot S3. This results in no axial force compressing the band, and therefore no force of the band is transmitted to the driven clutch. This allows a power source (such as an internal combustion engine) to operate at idle without transmitting torque to the driven clutch. In yet another embodiment (not shown), the slot S3 has a short portion S3B that is generally parallel to the axis of rotation and a constant angle behind the short portion S3B.

[0061] exist Fig.19 In yet another embodiment shown in , slot S5 has a first side S51, a second side S52, and a side S53. Sides S51 and S52 are oriented at different angles relative to the axis of rotation. Side S53 is generally perpendicular to the axis of rotation. Slot side S52 engages the pin during torque reversal (such as during engine braking), thereby allowing torque to be transferred in the opposite direction, i.e., from the driven clutch to the driving clutch.

[0062] As another embodiment Fig. 20As shown in , pin 33A and pin 33B are mated with one slot S6. Therefore, the load is distributed between the two pins, which allows for greater load transfer than when only one pin of the same size is mated with one slot. In some embodiments, pin 12 and pin 33 can be either a driven pin or a driving pin, depending on the position of the pin in the system.

[0063] exist Fig.21 In yet another embodiment shown in , the slots are angularly and axially spaced from each other. Slot S7A is axially shifted relative to slot S7B in direction D3. Shifting the slot positions axially relative to each other increases the distance DST between the slots, thereby allowing for a large slot angle SA7. Fig. 22 In another embodiment shown in , one side of the slot is open, wherein the angle of the first side S81 is different from the angle of the second side S82. In another embodiment (not shown), the actuator mechanism controls the driven clutch. In yet another embodiment (not shown), the drive clutch may include a spring. In some embodiments of the cam-controlled continuously variable transmission system, more than one pin may be engaged with at least one drive slot and at least one driven slot in a cooperative manner. In some embodiments, the positions of at least one drive slot and at least one driven slot may be axially displaced relative to each other. In other embodiments, at least one drive slot and at least one driven slot may have sides that are not parallel to each other. In yet another embodiment, at least one side of at least one drive slot and at least one driven slot is open.

[0064] In some embodiments, a cam-controlled continuously variable transmission system may include, but is not limited to, a drive clutch; a driven clutch connected to the drive clutch by a belt, wherein the belt surrounding the drive clutch and the driven clutch is positioned between a first drive sheave, a second movable drive sheave, a first driven sheave, and a second movable driven sheave; an actuator engaged with a carrier, wherein the carrier is rotatably journaled with a bearing, wherein the bearing is rotatably journaled with the second drive sheave for axially moving the second drive sheave, wherein a contact radius between the belt and the first and second driven and drive sheaves changes in response to input from the actuator, thereby accelerating or decelerating the driven clutch in a controlled manner relative to the drive clutch; at least one drive pin, wherein the at least one drive pin contacts a side of at least one drive slot to optimize force transmission from the belt; and at least one driven pin, wherein the at least one driven pin contacts a side of at least one driven slot to optimize force transmission from the belt. In some embodiments, the driving clutch may include, but is not limited to, a driving shaft; a first driving sheave fixed to the driving shaft; a second driving sheave movable parallel to the rotational axis of the driving shaft; and the second driving sheave is locked in rotational relation with the first driving sheave by a member cooperatively engaged with a second driving sheave receiving member, and the driving sleeve has at least one driving slot, and the at least one driving slot is arranged at a driving slot angle relative to the rotational axis of the driving shaft. In some embodiments, the driven clutch may include, but is not limited to, a driven shaft; a first driven sheave fixed to the shaft; a second driven sheave movable parallel to the rotational axis of the driven shaft; and the second driven sheave is locked in rotational relation with the first driven sheave by a member cooperatively engaged with a second driven sheave receiving member, and the driven sleeve has at least one driven slot, and the at least one driven slot is arranged at a driven slot angle relative to the rotational axis.

[0065] It can be understood from the above that, for the purpose of illustration, specific embodiments of the present invention have been described herein, but various modifications may be made without departing from the scope of the present invention. The features or elements of one embodiment may be used or exchanged with the features or elements of another embodiment. Therefore, the present invention is limited only by the appended claims.

[0066] Although the technology has been described in language specific to certain structures and materials, it should be understood that the invention defined in the appended claims is not necessarily limited to the specific structures and materials described. Instead, specific aspects are described as forms of implementing the claimed invention. Because many embodiments of the invention can be practiced without departing from the spirit and scope of the invention, the invention resides in the claims appended hereto.

[0067] Unless otherwise indicated, all numbers or expressions (such as those expressing dimensions, physical features, etc.) used in the specification (except for the claims) are understood to be modified by the term "approximately" or "about" in all cases. At least, and without attempting to limit the application of the doctrine of equivalents of the claims, each numerical parameter modified by the term "approximately" or "about" listed in the specification or claims should be interpreted at least in accordance with the number of significant digits listed and by applying rounding techniques. In addition, all ranges disclosed herein should be understood to include and support claims listing any and all subranges or any and all single values ​​contained therein. For example, the range of 1 to 10 should be considered to include and support claims listing any and all subranges or single values ​​between and / or including a minimum value of 1 and a maximum value of 10; that is, all subranges starting from a minimum value of 1 or greater and ending with a maximum value of 10 or less (e.g., 5.5 to 10, 2.34 to 3.56, etc.) or any value between 1 and 10 (e.g., 3, 5.8, 9.9994, etc.).

Claims

1. A cam-controlled continuously variable transmission system, comprising: A driving clutch, wherein the driving clutch comprises: Drive shaft; a first drive sheave secured to the drive shaft; a second drive sheave movable parallel to the axis of rotation of the drive shaft; the second drive sheave being locked in rotational relationship with the first drive sheave by a member cooperatively engaging a second drive sheave receiving member, the drive sleeve having at least one drive slot disposed at a drive slot angle relative to an axis of rotation of the drive shaft; a driven clutch connected to the drive clutch by a band, wherein the band surrounding the drive clutch and the driven clutch is positioned between the first drive sheave, the movable second drive sheave, the first driven sheave, and the movable second driven sheave, wherein the driven clutch comprises: Driven shaft; a first driven sheave fixed to the driven shaft; a second driven sheave movable parallel to the axis of rotation of the driven shaft; the second driven sheave being locked in rotational relationship with the first driven sheave by a member cooperatively engaged with a second driven sheave receiving member, the driven sleeve having at least one driven slot disposed at a driven slot angle relative to the rotational axis; an actuator engaged with a carrier, wherein the carrier is rotatably journaled with a bearing, wherein the bearing is rotatably journaled with the second drive sheave for axially moving the second drive sheave, wherein a contact radius between the belt and the first and second driven and driving sheaves changes in response to input from the actuator to thereby controllably accelerate or decelerate the driven clutch relative to the driving clutch; at least one drive pin that contacts a side of at least one drive slot to optimize force transfer from the belt; and At least one follower pin contacts a side of at least one follower slot to optimize force transfer from the band.

2. The cam-controlled continuously variable transmission system according to claim 1, wherein: The carrier is a driving carrier.

3. The cam-controlled continuously variable transmission system according to claim 1, wherein: The carrier is a driven carrier.

4. The cam-controlled continuously variable transmission system according to claim 1, wherein: The bearing is a thrust bearing.

5. The cam-controlled continuously variable transmission system according to claim 1, wherein: The driving slot angle and the driven slot angle are constant.

6. The cam-controlled continuously variable transmission system according to claim 1, wherein: The driving slot angle and the driven slot angle have variable angles.

7. The cam-controlled continuously variable transmission system according to claim 5, wherein: The starting angle in the drive clutch is approximately 16 degrees at the first end of at least one drive slot and gradually increases to an angle in the range of 38 degrees at the second end of the at least one drive slot, and the starting slot angle in the at least one driven slot is in the range of approximately 60 degrees at the first end and gradually decreases to an angle in the range of 35 degrees at the second end of the at least one driven slot.

8. The cam-controlled continuously variable transmission system according to claim 1, wherein: A first portion of the at least one drive slot is parallel to the axis of rotation.

9. The cam-controlled continuously variable transmission system according to claim 1, wherein: The actuator is engaged with the carrier via a linkage that is rotatably journalled with the carrier.

10. The cam-controlled continuously variable transmission system of claim 1, wherein: The actuator is engaged with the carrier via an eccentric, wherein the eccentric is rigidly attached to an output shaft of the actuator and cooperatively engaged with the carrier.

11. The cam-controlled continuously variable transmission system of claim 1, wherein: The actuator comprises a screw for force multiplication.

12. The cam-controlled continuously variable transmission system of claim 1, wherein: The actuator actuates the second drive sheave.

13. The cam-controlled continuously variable transmission system of claim 1, wherein: The actuator is configured to move the second driven sheave axially along the driven shaft.

14. The cam-controlled continuously variable transmission system of claim 1, wherein: The force applied by the actuator generally corresponds to the contact area between the belt and the second drive sheave and the second driven sheave, thereby counteracting the force of the belt acting on the second drive sheave and the second driven sheave.

15. The cam-controlled continuously variable transmission system of claim 1, wherein: One or more pins cooperatively engage the at least one drive slot and the at least one driven slot.

16. The cam-controlled continuously variable transmission system of claim 1, wherein: The positions of the at least one drive slot and the at least one driven slot are axially displaced relative to each other.

17. The cam-controlled continuously variable transmission system of claim 1, wherein: At least one drive slot and at least one driven slot have sides that are non-parallel to each other.

18. The cam-controlled continuously variable transmission system of claim 1, wherein: At least one side of at least one driving slot and at least one driven slot is open.

19. The cam-controlled continuously variable transmission system of claim 1, wherein: The drive shaft is connected to a bicycle crank.

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